Ring oscillator



Nov. 18, 1958 B. Toccl-GUILBERT 2,860,495

RING osCILLAToR Filed April 1s, 1955 INVENTOR. iPA/i bcc/-maier i l i i i i i i i i United States Patent RING oscrLLA'roR Application April 13, 1955, Serial No. 501,053

8 Claims. (Cl. 64-13) This invention relates to improvements in oscillating couplings, between a rotating stub shaft and a working surface, and, more particularly, to a ring-type oscillator by which the advantages are obtained for substantially larger surfaces than theretofore possible.

Oscillators of the `type shown in United States Letters Patent Nos. 2,486,078, 2,629,990, and 2,633,008, and oscillating back pads shown in United States Letters APatentNos. 2,666,281 and 2,681,532, are quite satisfactory for portable tools and small machine tools, requiring an abrasive surface of not over nine inches in diameter. However, where larger diameters are required, peripheral speeds are such that it is dangerous to employ hand tools, and, further, the leverage caused by any pressure at the periphery is diicult to control by a rela-- tively small resilient mass adjacent the shaft. Further, it has not been found satisfactory to increase the size of the previous oscillators for this purpose as it has been discovered that only a very small portion of the mass is lrequired to accomplish the result desired and that rotating any more than the required mass is wasteful and costly.

Accordingly, it is an object of the present invention to produce a ring type oscillator which will incorporate the advantages of the central mass type, but provide re- ',siliency only at the areas where the optimum activity occurs.

It is a further object of the present invention to produce an oscillator for rotating abrasives of diameters larger than nine inches.

Because of the additional speeds and weights required in larger sizes, it is also an object of the present invention to produce an oscillator which is completely safe, and yet one where the resilient mass operates in shear.

It is a lfurther object of the invention to produce a 'ring-type oscillator which is a unitary structure, completely fabricated as an integral unit before attachment to the rotating shaft or motor.

Still another objectvof the-present invention is to se- ,cure' the benefits of nutating motion in large horizontally rotating grinders and Sanders without increasing the over-all height of the machine and at the same time provide greater stability.

Another object is to provide a machine which not only produces a lapping action but also a variable lapping action in proportion to the pressure applied to the abrading head, all of which can be accomplished at high rotational speeds.

Further objects are to provide a construction of maX- imum simplicity, economy and ease of assembly and disassembly, also such further objects, advantages and capabilities as will fully appear and as are inherently possessed by the device and the invention described herein.

The invention further resides in the combination, construction and arrangement of parts illustrated in the accompanying drawings, and while there is shown there a preferred embodiment and one variant thereof, it is to be understood that the same are merely illustrative of the invention and that the invention is capable of modiiication and change, andcomprehends other details of construction without departing from the spirit thereof, or the scope of the appended claims.

Referring to the drawings:

Figure 1 is a vertical sectional view of a ring oscillator secured to the driving member of a vertical motor and attached to the rotating face plate of a floor sander and polisher; and

Figure 2 is a vertical section of a variant form of ring oscillator attached to a hub flange and a coupler flange, ready for attachment to the drive shaft of a motor or the like.

Referring now to the drawings, in which like reference numerals indicate like parts in the several views, and referring particularly to Figure 1, there is shown generally at 10 a ring oscillator of the present invention. The ring oscillator is composed of two identical nonresilient ring members 11 and 12, each of which has an outer plane surface 14 and 15, respectively, and marginal up- Vstanding flanges 16 and 17, 18 and 19, respectively.

These marginal anges are undercut as at 20, so that at their bases the wall is thinner than at the top. In the fabrication of the ring oscillator 10, the rings 11 and 12 are placed so that their flanges are opposed to each other and are spaced from each other by a solid, resilient material 22, such as natural or synthetic rubber. Rubber having a durometer of 55 appears to produce optimum results for most purposes. The resilient material is vulcanized or otherwise bonded to the two ring members and spaces them apart by a continuous central radial portion 23, which covers the full distance from the inner to the outer diameter. This is the shear zone and also a compression zone Where the opposed marginal anges 16 andl 18, and 17 and 19, operate. With the bonding of the resilient material 22 to the rings 11 and 12, it is apparent that a single unitary nonseparable structure is produced in which there is no metal-to-metal contact, and in which the resilient material, because of the undercutting 20, is keyed in place.

For attachment to the mechanism for sanding, polishing, or the like, the upper and lower surfaces 14 and 15 of the ring oscillator 10 are bored and tapped as at 24 and 25 to receive machine screws such as 26 and 27. Hub flange 28 is secured to the top surface 14 of the ring oscillator through holes 30 registering with the bores 24, through which are passed the machine screws 26. The ring oscillator 10 tits within a recessed shoulder 31 in the under surface of the hub flange 28, so that it is firmly retained in a nonchattering position. The hub llange 28 is in turn securely fastened to the drive head 32 of a motor (not shown) for rotation therewith, by any suitable means, s uch as by the retaining nut 33. Thus, the upper nonresilient member 11 is rigidly and directly connected to the drive head 32.

On the lower face 15 of the ring oscillator 10, the coupling flange 34 is secured in a similar manner to that of the hub flange 28. Holes 35 are placed in the radial portion 36 of the flange 34 to register with the bored and tapped holes 25, which receive the machine screws 27 and fasten the ring oscillator 10 securely in position thereon. The inner face of the coupler flange 34 likewise has a recessed shoulder 37, which engages the suitable working surface may be secured to the face plate 40.

It will be observed that when the ring oscillator is in position as shown in Figure 1, and rotated without the working surface being in contact with a floor or the like, the rotation will be concentric and substantially no difference will be noticed in the rotation with the oscillator in place than that when the oscillator is omitted and Vwhen there is rnetal-to-metal rigid connection between the driving head of the motor and the face plate 40, as has been the previous practice. However, when the working surface 44 is applied to the oor or the like, then the rotation exhibits the startlingly diiferent combined gyroscopic and undulating motions with the same nutative features and benets as are obtained with the earlier oscillators. The larger surface area of the face plate 40 means that this substantially unyielding surface will bridge the low spots and will tend to smooth off the high spots down to the level of the low spots, making the under surface even. Differences in the altitude of the high spots are compensated by the compression of the resilient material 22 during rotation which rapidly changes location in the resilient material 22 as the face plate is moved over the floor. Any irregularities in altitude or otherwise are not transmitted to the drive head 32 or shaft of the motor because they are immediately absorbed and compensated for in the resiliency of the n material 22. Thus, the wear on the motor and bearings due to axial distortion is greatly reduced and much of the cause for service lay-ups and maintenance expense are eliminated.

In addition, since the resilient material 22 operates most efficiently in shear, the ring oscillator is operating at optimum eiciency when rotated as described, with the working surface in contact with the Hoor. It will be observed that in the area indicated as 23, the resilient material extends the full width of the ring oscillator to permit operation in shear. Frictional torque of operating contact induces shear, as well as the centrifugal force of rotation.

It will be noted that there is no metal-to-metal or rigid coupling between the driving head 32 of the motor and the face plate 40, because of the interposition of the ring oscillator 10. During rotation in the manner described the frictional torque set up by the contact of the work surface 44 and the floor is transmitted to the resilient material 22. The resilience of the material 22 results in a difference in rotation between the xed portion, being member 1l, hub ange 2S and the motor drive head 32, and that of the face plate 40, the coupling tiangeA 34 and the member 12. The rotation of the face plate is in a constantly changing and never recurring orbit, as well as a wavy rotation in varying vertical planes, which complex motion, for want of a better term, has been called nutative motion. It is only by means of this nutative motion that it is possible to sand or polish with the entire face of the face plate 40 at high speeds and without any danger of scoring or making concentric rings or marks. Likewise, the resilient coupling providedby the ring oscillator eliminates vibration and the possbility of the working surface digging into the oor and leaving ugly mars. The nonrecurring orbit of rotation prevents the fouling and filling of the work surface 44, making the same longer lasting and more eflicientl over its life. In addition, there is no possibility of producing ahill and dale surface as is common with drum Sanders.

Referring now to Figure 2, the ring oscillator is composed of an upper nonresilient member 50, having a d'e`- pending outer peripheral fiange 51 and an inturned radial ange S2. It may be provided with an inwardly directed boss 53 which is tapped and threaded as at 54. It has an opposed nonresilient member 55, having an upstanding inner peripheral flange 56 with an inturned radial flange 57. This likewise may be provided with an inwardly directed boss 58, tapped and threaded as at 60. Resilient material 61 separates the two nonresilient members and 55 and is vulcanized thereto, or bonded in any other suitable manner so that the resilient and n-onresilient portions become an integral, nonseparable unit in the form of a ring of substantial thickness. The inturned ilanges 52 and 57 key the resilient material in position and help resist any breakdown of the bond. The resilient material 61 is preferably natural rubber of durometer, although any other suitable material may be used, such as synthetic rubber. It will be noticed that the resilient material is in shear, although the shear may be offset and extend at a diagonal from the lower, outer periphery to the inner, upper periphery. This shear zone is also the compression zone 62 provided in the resilient material between the inturned ange 52 and the opposed portion of the member 55. On the inner periphery there is a compression zone 63 between the inturned radial flange 57 and the inner surface of the member 50.

Obviously, the upper nonresilient ring 50 may be provided with an inner peripheral ange instead of the ange 51, and nonresilient ring member 55 with an outer peripheral flange instead of flange 56. However, better operating characteristics are secured by making the ring oscillator in the manner shown in Figure 2.

The ring oscillator of Figure 2 is attached to the hub viiange 64 in a similar manner as that described in connection with the oscillator 10 of Figure 1.

vIn this instance, however, the hub flange 64 is keyed to the motor shaft for rotation as a unit therewith, by means of keyway 65, establishing a rigid metal-to-metal connection between the motor shaft, the hub 64 and the member 50. Likewise, the coupler flange is secured to the lower surface or member 55 in the same manner as the coupler plate 34 is attached to the ring oscillator 10 of Figure l. A rigid metal-to-metal connection between the face plate 40, the coupler ange 70, and the nonresilient member 55. However, the interposition of the ring oscillator unit does away with any rigid, metalto-metal connection between the drive and the working surface.

It will be observed that the same nutative movement is obtained when the oscillator of Figure 2 is rotated in conjunction with a face plate and suitable working surface in contact with the oor or the like. Precisely the same beneiits resulting from said motion are secured,

only it may be observed that the additional mass of resilient material 61 will produce a livelier and more sensitive complex motion than can be expected of the oscill lator 10 of Figure l.

In rotating an abrasive disc for sanding or grinding in the larger machines here contemplated, gear trains are required to get themy up to speed and also to reduce the speed of the motor, as these machines have formerly i had very restricted operating speeds. It is apparent that the ring oscillators here disclosed may be used with gear i trains without increasing the over-all height of the machine. The central opening provides the necessary space for gears and the like. Likewise, the rotation of the 3 mass of the ring oscillator tends to produce a gyroscopic 1 action and materially increases the stability of operation.

Further, the fact that the frictional torque is trans-` mitted through a mass of resilient material, without i metal-to-metal contact, reduces the requirement for gears. t The sudden torque and grab naturally encountered ini starting and contact with a surface is converted into al myriad ofv minute-oscillations by the ring oscillator and is not transmitted tothe motorA or shaft bearings. Thus, the use of a ring oscillator does away with the necessity f o'r `elaborate gear trains. Likewise, the ring oscillator in distributing a relatively small mass of resilient material over the widest area possibleV provides maximum stability with a minimum amount of mass.

Further, in operation, even without contact with a surface, the ring oscillator produces, to a small degree, the characteristics of nutative motion. However, on contact the frictional torque adds a condition which insures lapping, or nonconcentric rotary motion, but with the added benefits of undulation. The greater the pressure, up to optimum operation, the greater frictional torque, and the greater the lapping.

The ring oscillator releases the speed limitations of operation with gear trains and single speed lapping. The present devices have been operation tested at speeds varying from 150 R. P. M. to 8,000 R. P. M. with the highest speeds producing the best results.

I claim:

l. A ring resilient coupling for coaxial attachment as a unit between a drive shaft defining a common axis and a driven member comprising a rst nonresilient narrow ring member having at least one axial peripheral iiange, a second and opposed nonresilient ring member of substantially the same inner and outer diameters as said first member having at least one axial peripheral fiange, and a body of resilient material between said two ring members of substantially the same inner and outer diameters'as the ring members, bonded and keyed theretogether to form a nonseparable unitary structure with a portion of said resilient material being exposed along the inner and outer periphery and with no direct contact between said ring members the inner periphery of said coupling being spaced a substantial distance from said common axis.

2. A coupling for coaxial attachment as a unit between a motor drive shaft defining a common axis and a driven member comprising a first metallic ring member having at least one marginal iiange, a second metallic ring member of substantially the same diameters as said first ring member having at least one marginal iiange, said ring members being spaced and opposed to each other with their marginal flanges directed toward the opposite ring member, and a body of rubber between said twoY metallic members of substantially the same diameters as said ring members, bonded and keyed thereto to form a unitary structure with a portion of said resilient material being exposed along the inner and outer periphery and with no metal-to-metal contact between said metallic ring members the inner periphery of said unit being spaced a substantial distance from the common axis.

3. A resilient torque unit for coaxial coupling between a drive shaft defining a common axis and a driven member, a first solid metallic ring member having marginal flanges extending axially from one face thereof, a second and substantially identical ring member spaced from said first member with its marginal anges in opposed position to said first ring member, and a body of resilient material separating said metallic ring members, bonded and keyed thereto to form a nonseparable unitary structure with a portion of said resilient material being exposed along the inner and outerv periphery and with no metal-to-metal contact between said ring members or flanges said coupling unit having its inner periphery spaced a substantial distance from the common axis.

4. A resilient torque unit for rotary coaxial coupling between a drive shaft defining a common axis of rotation and a driven member, a first continuous narrow metallic ring member having continuous marginal flanges extending axially from one face thereof, a second and substantially identical ring member spaced fronirsaid firstimemberv with its marginal flanges in opposed position, and a body of resilient material separating said metallic ring members, bonded and keyed thereto to form a nonseparable unitary structure with a portion of said resilient material being exposed along the inner and outer peripheryA and with no metal-to-metal lcontact between said ring members or fianges the inner perimeter of said torque unit being spaced at a substantial distance from said common axis.

5. A resilient torque unit for rotary coaxial coupling between a drive shaft defining the axis of rotation and a driven member, a first continuous metallic ring member having continuous marginal iianges extending axially from one face thereof and with inwardly Wider termini for assisting in the locking or keying of the resilient body material, a second and substantially identical ring member spaced from said first member with its marginal iianges in opposed position, and a body of resilient material separating said metallic ring members, bonded and keyed thereto to form a nonseparable unitary structure with no metal-to-metal contact between said ring members or flanges the inner periphery of said torque unit being spaced a substantial distance from said axis of rotation.

6. A resilient torque unit for coaxial coupling between a drive shaft defining a common axis of rotation and a driven member, a first continuous metallic ring member having continuous marginal fianges extending axially from one face thereof and with inwardly wider termini for assisting in the locking or keying of the resilient body material, a second and substantially identical ring member spaced from said first member with its marginal flanges in opposed position, a body of resilient material separating said metallic ring members, bonded and keyed thereto to form a nonseparable unitary structure with no metal-to-metal contact between said ring members or flanges the inner periphery of said torque unit being spaced substantially from said common axis, means associated with said first ring for coupling to a drive shaft, and means associated with said second ring for coupling to a driven member.

7. A resilient torque unit for coaxial coupling between a drive shaft defining a common axis of rotation and a driven member with a rotary working face, a first continuous metallic ring member having an outer marginal flange extending axially from one face thereof, a second continuous metallic ring member of substantially the same diameter having an inner marginal flange extending axially from one face thereof said ring members being spaced from each other and with the outer faces of their respective anges being directed toward the opposite member, and a body of rubber between said metallic ring members bonded and keyed thereto and said anges to form a unitary structure of uniform diameters and with no metal-to-metal contact between said ring members or their iianges the inner periphery of said torque unit being spaced a substantial distance from said common axis.

8. A resilient torque unit for coaxial coupling between a drive shaft defining a common rotary axis and a driven i member having a working face, a first continuous metallic ring member having an outer marginal flange extending axially from one face thereof and having an inturned radial terminal flange, a second continuous metallic ring member of substantially the same inner and outer diameters having an inner marginal ange extending axially from one face thereof and having an inturned radial terminal flange, said ring members being spaced from each other and with the outer faces of their respective flanges being directed toward the opposing ring member, and a body of rubber between said metallic ring members bonded and keyed thereto and said flanges to form a unitary structure of uniform diameters and with no metal-to-metal contact between said ring members or thei-ranges said torque unit having anv inner periphery spaced a substantialdistance fromz said common axis.

References Cited in the filf this patent Julien Sept. 12, 1-939 8 Moser O ct. 101944 Worley e ,Ju1y 6 1948` lessop A .ASept. 21 1248 Tocci-Guilbert O c t. 25A, 1949 Tocci-Guilbert Mar. 3, 1953 FOREIGN PATENTS Great Britain Feb. 19, 1945 

